CA2491230A1 - Overrunning alternator decoupler pulley with bare wire spring and grease lubrication - Google Patents
Overrunning alternator decoupler pulley with bare wire spring and grease lubrication Download PDFInfo
- Publication number
- CA2491230A1 CA2491230A1 CA002491230A CA2491230A CA2491230A1 CA 2491230 A1 CA2491230 A1 CA 2491230A1 CA 002491230 A CA002491230 A CA 002491230A CA 2491230 A CA2491230 A CA 2491230A CA 2491230 A1 CA2491230 A1 CA 2491230A1
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- Canada
- Prior art keywords
- hub
- pulley
- carrier
- set forth
- decoupler assembly
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D41/00—Freewheels or freewheel clutches
- F16D41/20—Freewheels or freewheel clutches with expandable or contractable clamping ring or band
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/32—Friction members
- F16H55/36—Pulleys
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B67/00—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for
- F02B67/04—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for of mechanically-driven auxiliary apparatus
- F02B67/06—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for of mechanically-driven auxiliary apparatus driven by means of chains, belts, or like endless members
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/50—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members
- F16D3/72—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members with axially-spaced attachments to the coupling parts
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D41/00—Freewheels or freewheel clutches
- F16D41/20—Freewheels or freewheel clutches with expandable or contractable clamping ring or band
- F16D41/206—Freewheels or freewheel clutches with expandable or contractable clamping ring or band having axially adjacent coils, e.g. helical wrap-springs
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/32—Friction members
- F16H55/36—Pulleys
- F16H2055/366—Pulleys with means providing resilience or vibration damping
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Pulleys (AREA)
- Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
- Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
- Electrical Discharge Machining, Electrochemical Machining, And Combined Machining (AREA)
- Springs (AREA)
- Lubricants (AREA)
Abstract
A decoupler assembly (20) is provided for allowing an alternator to be rotatably driven by a serpentine belt (14) in an engine of an automotive vehicle and for allowing the speed of the belt to oscillate relative to the alternator. A hub is fixedly carried by a drive shaft (15) from the alternator for rotation therewith. A pulley (50) is rotatably journaled to the hub by a ball bearing member (55). The ball bearing member includes lubricant for minimizing frictional wear therein. A bare, helical clutch spring (71) is operatively coupled between the hub and pulley for transferring rotational movement from the pulley to the hub during acceleration of the pulley relative to the hub by the serpentine belt and for allowing the hub to overrun the pulley during deceleration of the pulley relative to the hub.
Description
OVERRUNNING ALTERNATOR DECOUPLER PULLEY WITH BARE WIRE
SPRING AND GREASE LUBRICATION °
Field of the Invention The invention relates to a belt drive assembly for driving belt driven accessories in an engine of an automotive vehicle, and more particularly, to a decoupling mechanism for allowing the belt driven accessories to operate temporarily at a speed other than the belt drive assembly.
Description of the Prior Art It is widely known in an automotive vehicle engine to transfer a portion of the engine output to a plurality of belt driven accessories utilizing an endless serpentine belt. Typically, each component includes an input drive shaft and a pulley coupled to a distal end of the drive shaft for driving engagement with the belt. An example of such a belt driven accessory is an alternator.
It is also known to provide a decoupler operatively coupled between the pulley and the alternator to allow the alternator drive shaft to "overrun" or rotate at a faster speed than the pulley and to allow the speed of the pulley to oscillate with respect to the alternator drive shaft due to oscillations in the engine speed.
Examples of decouplers are disclosed in the United States Patent 6,083,130, issued to Mevissen et al. on July 4, 2000 and the United States Patent 5,139,463, issued to Bytzek et al.
on August 18, 1992.
It remains desirable to provide a decoupler that is easier to manufacture and has better durability over conventional de,coupler designs.
SUBSTITUTE SHEET (RULE 26) SLTNIMARY OF THE INVENTION
According to one aspect of the invention, a decoupler assembly is provided for transfernng torque between a shaft and a drive belt. The decoupler assembly includes a hub configured to be fixedly secured to the shaft. The hub includes a helical first slot formed therein. A earner is rotatably mounted on the hub. The carrier includes a helical second slot formed therein. A torsion spring extends between a hub end and a carrier end for transfernng torque between the hub and carrier, wherein the hub end is retained in the helical first slot to prevent relative movement between the hub end of the torsion spring and the hub and the carrier end is retained in the helical second slot to prevent relative movement between the earner end of the torsion spring and the earner. A pulley is rotatably coupled to the hub. The pulley includes an outer surface configured to frictionally engage with the drive belt. The pulley has an inner surface formed therein. A clutch spring is fixedly secured to the carrier and has a plurality of helical coils frictionally engaging with the inner surface of the pulley to selectively couple the hub and pulley. The torsion spring and the clutch spring are wound in opposite senses enabling the clutch spring to expand into gripping engagement with the inner surface during acceleration of the pulley relative to the hub and to contract out of gripping engagement with the inner surface during deceleration of the pulley relative to the hub.
BRIEF DESCRIPTION OF THE DRAWINGS
Advantages of the present invention will be readily appreciated as the same becomes better understood by reference to the following detailed description when considered in connection with the accompanying drawings wherein:
Figure 1 is a front view of an engine of an automotive vehicle incorporating a decoupler assembly according to one. aspect of the invention;
Figure 2 is an enlarged fragmentary sectional view of the decoupler assembly;
Figure 3 is a perspective view of a clutch spring in the decoupler assembly;
Figure 4 is a perspective view of a earner for carrying one end of the clutch spring in the decoupler assembly;
Figure 5 is a perspective view of the clutch spring assembled to the carrier;
Figure 6 is an exploded perspective view of the decoupler assembly according to a second embodiment of the invention;
Figure 7 is a cross sectional view of the decoupler assembly according to the second embodiment of the invention; and Figure 8 is a cross sectional view of the decoupler assembly according to a third embodiment of the invention.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT
Referring to the figures, an engine for an automotive vehicle is generally indicated at 10 in Figure 1. The engine 10 includes a crankshaft 12 driving an endless serpentine belt 14, as commonly known by those having ordinary skill in the a.rt. The engine 10 also includes a belt~driven accessory 16 driven by the belt 14. Described in greater detail below, a decoupler assembly 20 is operatively assembled between the belt 14 and the belt driven accessory 16 for automatically decoupling the belt driven accessory 16 from the. belt 14 when the belt 14 decelerates relative to the belt driven accessory 16 and allowing the speed of the belt 14 to oscillate relative to the belt driven accessory 16. Additionally, a detailed description of the structure and function of a decoupler assembly can be found in applicant's United States Patent 6,083,130, which issued on July 4, 2000 and is incorporated herein by reference in its entirety.
Referring to Figure 2, the decoupler assembly 20 includes a hub 22 having opposite.
first 24 and second 26 ends and a generally cylindrical body 28 extending axially therebetween. The body 28 includes opposite inner 30 and outer 32 surfaces extending between the first 24 and second 26 ends of the hub 22. The inner surface 30 includes a plurality of inner threads 33 adjacent the first end 24 for fixedly securing the hub 22 to a drive shaft 15 from the belt driven accessory 16. A reduced diameter portion 34 is formed in the first end 24. The reduced diameter portion 34 includes an outer mounting surface 36 having a smaller outer diameter than the body 28. An abutment surface 38 opposite the second end 26 extends generally radially between the outer mounting surface 36 and the body 28. An annular thrust washer 39 is seated on the outer mounting surface 36 adjacent the abutment surface 38.
A socket 40 is formed in the second end 26 for receiving a suitable tool therein for rotatably threading the hub 22 onto the drive shaft 15. An annular first flange 41 extends radially outwardly from the body 28 adjacent the second end 26. The first flange 41 includes an outer flange surface 42 having a larger outer diameter than the body 28. An annular surface 44 extends generally radially between the body 28 and the outer flange surface 42 opposite the second end 26. A generally helical first slot 46 is formed in the annular surface 44 defining a first locating surface 48 therein.
A generally cylindrical pulley 50 is rotatably journaled to the hub 22. More specifically, the pulley 50 extends between opposite first 52 and second 54 ends. The pulley 50 includes an inner surface 56 extending between the first 52 and second 54 ends. A ball ?0 bearing member 57 is coupled between the pulley 50 and the hub 22. The bearing member 57 includes an inner race 58 fixedly secured to a portion of the outer mounting surface 36 and an outer race 59 fixedly secured to a portion of the inner surface 56 adjacent the first end 52 of the pulley 50. A plurality of ball bearings 55 is rollingly engaged between the inner 58 and outer 59 races of the bearing member 57. A cylindrical bushing 60 is journal mounted between the pulley 50 and the first flange 41. The bushing 60 includes a sleeve wall 62 extending between a portion of the inner surface 56 adjacent the second end 54 and the outer flange surface 42 of the first flange 41. A bushing bushing flange 64 extends radially inwardly from the sleeve wall 62 and abuts the annular surface 44 in the first flange 41.
The pulley 50 includes an outer periphery 66 with a plurality of V-shaped grooves 68 formed therein for rollingly engaging and guiding the belt 14.
Referring to Figures 2-5, a one-way clutch assembly 70 is operatively coupled between the hub 22 and the pulley 50. The clutch assembly 70 includes a clutch spring 71 and a carrier 75. The clutch spring 71 includes a plurality of helical coils 72 extending between a bent or hooked proximal end 73 and an opposite distal end 74.
Preferably, the clutch spring 71 is formed from an uncoated, spring steel material and has a non-circular cross-section to improve frictional contact. Most preferably, the cross-section of clutch spring 71 is rectangular or square. The clutch spring 71 is press fitted into frictional engagement with the inner surface 56 of the pulley 50. Preferably, a lubricant similar or compatible with grease used in the ball bearing member 57 is applied to minimize wear between the clutch spring 71 and the inner surface 56 of the pulley 50.
The carrier 75 is rotatably mounted on the hub 22. The carrier 75 is generally ring shaped and extends axially between opposite first and second sides 76, 78. A
hooked slot 84 is formed in the second side 78 of the carrier 75 and is configured to retain the hooked proximal end 73 of the clutch spring 71. A generally helical second slot 86 is formed in the second side 78 of the carrier 75 defining a second locating surface 88 generally opposing the first locating surface 48 formed in the annular surface 44.
Referring to Figure 2, a helical torsion spring 90 extends between hub 92 and earner 94 ends. The torsion spring 90 is axially compressed between the first 48 and second 88 locating surfaces for transferring torque between the hub 22 and the carrier 75. More specifically, the hub end 92 of the torsion spring 90 is retained in the first slot 46 of the hub 22. Similarly, the earner end 94 of the torsion spring 90 is retained in the second slot 86 in the second side 78 of the earner 75. Axial forces due to the compression of the torsion spring 90 retains the first side 76 of the earner 75 in abutting engagement with the thrust washer 39.
The torsion spring 90 also allows relative movement between the earner 75 and the hub 22 to accommodate changes in the speed of the pulley 50 due to generally oscillating changes in the operating speed of the engine. The torsion spring 90 and the clutch spring 71 are coiled in opposite directions.
A cap 100 is fixedly assembled to a flange 102 formed in the pulley 50 for preventing contaminants from entering the decoupler assembly 20 and for retaining the lubricant within the decoupler assembly 20.
In operation, the engine 10 is started and the pulley 50 is accelerated and rotated in a driven direction by the belt 14 driven by the engine 10. Acceleration and rotation of the pulley 50 in the driven direction relative to the hub 22 creates friction between the inner surface 56 of the pulley 50 and preferably all of the coils 72 of the clutch spring 71. It should be appreciated that the clutch spring 71 will function even where at the onset at least one of the coils 72 of the clutch spring 71 is frictionally engaged with the inner surface 56 of the pulley 50. The clutch spring 71 is helically coiled such that the friction between the inner surface 56 of the pulley 50 and at least one of the coils 72 would cause the clutch spring 71 to expand radially outwardly toward and grip the inner surface 56 of the pulley 50. Continued rotation of the pulley 50 in the driven direction relative to the hub 22 would cause a generally exponential increase in the outwardly radial force applied by the coils 72 against the inner surface 56 until all of the coils 72 of the clutch spring 71 become fully brakingly engaged with the pulley 50. When the clutch spring 71 is fully engaged with the inner surface 56, the rotation of the pulley 50 is fully directed toward rotation of the drive shaft 15 of the belt driven accessory 16. Additionally, centrifugal forces help to retain the clutch spring 71 in braking engagement with the inner surface 56 of the pulley 50.
The rotational movement of the carrier 75 in the driven direction is transferred to the hub 22 by the torsional spring 90 such that generally the earner 75, thrust washer 39, hub 22, and the drive shaft 15 from the belt driven accessory 16 rotate together with the pulley 50.
Additionally, the torsional spring 90 resiliently allows relative movement between the carrier 75 and the hub 22 to accommodate oscillations in the speed of the pulley 50 due to corresponding oscillations in the operating speed of the engine 10.
When the pulley 50 decelerates, the hub 22 driven by the inertia associated with the rotating drive shaft 15 and the rotating mass within the belt driven accessory 16 will initially "overrun" or continue to rotate in the driven direction at a higher speed than the pulley 50.
More specifically, the higher rotational speed of the hub 22 relative to the pulley 50 causes the clutch spring 71 to contract radially relative to the inner surface 56 of the pulley 50. The braking engagement between the clutch spring 71 and the pulley 50 is relieved, thereby allowing overrunning of the hub '22 and drive shaft 15 from the belt driven accessory 16 relative to the pulley 50. The coils 72 may remain frictionally engaged with the inner surface 56 while the pulley 50 decelerates relative to the clutch assembly 70 and the hub 22. The coils 72 of the clutch spring 71 begin to brakingly reengage the inner surface 56 as the pulley 50 accelerates beyond the speed of the hub 22.
Referring to Figures 6 and 7, a second embodiment of the decoupler assembly 20' is shown, wherein elements of the alternative embodiment similar to those in the first embodiment are indicated by primed reference characters. The decoupler assembly 20' is assembled between an output or cranlahaft 106 of an engine and the belt 14' to allow the belt 14' to overrun the crankshaft 106. The decoupler assembly 20' includes a generally rinb shaped spring support 110. The slot 46' of the hub 22' has a generally U-shaped cross section for retaining the spring support 110 therein.
A first tab 112 extends outwardly from the spring support 110. A first notch 114 is formed in the hub end 92' of the torsion spring 90' for axially receiving the first tab 112 therein. Engagement between the first tab 112 and the first notch 114 prevents relative rotational movement of the hub end 92' of the torsion spring 90' relative to the spring support 110 and hub 22'. Similarly, a second tab 116 extends outwardly from the second locating surface 88' of the carne.r 75'. A second notch 118 is formed in the carrier end 94' of the torsion spring 90' for axially receiving the second tab 116 therein.
Engagement between the second tab 116 and the second notch 118 prevents relative rotational movement of the carrier end 94' of the torsion spring 90' relative to the carrier 75'.
The pulley 50' includes an outer periphery 120 for seating the belt 14' therein and an inner flange portion 122. The inner flange portion 122 has a generally U-shaped cross section defined by outer 124 and inner 126 pulley walls and a first connecting wall 12S
extending radially therebetween. The cawier 75' is retained between the outer 124 and inner 126 pulley walls and the first connecting wall 128 of the inner flange portion 122, such that the carrier 75' rotates with the pulley 50'. A second connecting wall 130 extends radially between the outer pulley wall 124 and the outer periphery 120.
The earner 75' includes a slot or split 132, which helps the carrier 75' to flex and accommodate loads associated with the rotation of the decoupler assembly 22'.
Referring to Figure 8, a third embodiment of the decoupler assembly 20" is shown, wherein the body 28" and first flange 41" of the hub 22" are fornled separately and fixedly connected in a subsequent assembly operation. The body 28" of the hub 22" is generally cylindrical and extends between the first 24" and second 26" ends. The first flange 41"
includes a mounting portion 140, which has a center bore 142 for receiving the outer flange surface 36" of the hub 22" therethrough. The first flange 41" includes a generally U-shaped cross section defined by an end wall 134 extending radially between generally parallel inner 136 and outer 138 flange walls. The spring support 110" is retained between the inner 136 and outer 138 flange walls and the end wall 134, such that the spring support 110" rotates with the first flange 41 ".
The outer periphery 120" and the inner flange portion 122" of the pulley 50"
are formed separately and fixedly connected in a subsequent assembly operation using any suitable method, such as welding. The generally U-shaped cross section of the inner flange portion 122" opens toward the first flange 41". The carrier 75" is retained between the outer 124" and inner 126" pulley walls and the first connecting wall 128", such that the carrier 75"
rotates with the pulley 50".
A ring plate 143 is mounted concentrically onto the outer mounting surface 36"
adjacent the abutment surface 38". A thrust washer 144 is disposed between the first flange 41" and the ring plate 143. The thrust washer 144 is axially spaced apart from the end wall 134 of the flange 41" for receiving the inner flange portion 122" of the pulley 50"
therebetween.
A torsional vibration damper 146, as known by those skilled in the art, is fixedly secured to the outer flange wall 138 of the first flange 41" for dampening vibrations experienced at the crankshaft 106 associated with the operations of the engine.
The invention has been described in an illustrative manner, and it is to be understood that the terminology, which has been used, is intended to be in the nature of words of description rather than of limitation. Many modification and variations of the present invention are possible in light of the above teachings. It is, therefore, to be understood that within the scope of the appended claims, the invention may be practiced other than as ~ specifically described.
SPRING AND GREASE LUBRICATION °
Field of the Invention The invention relates to a belt drive assembly for driving belt driven accessories in an engine of an automotive vehicle, and more particularly, to a decoupling mechanism for allowing the belt driven accessories to operate temporarily at a speed other than the belt drive assembly.
Description of the Prior Art It is widely known in an automotive vehicle engine to transfer a portion of the engine output to a plurality of belt driven accessories utilizing an endless serpentine belt. Typically, each component includes an input drive shaft and a pulley coupled to a distal end of the drive shaft for driving engagement with the belt. An example of such a belt driven accessory is an alternator.
It is also known to provide a decoupler operatively coupled between the pulley and the alternator to allow the alternator drive shaft to "overrun" or rotate at a faster speed than the pulley and to allow the speed of the pulley to oscillate with respect to the alternator drive shaft due to oscillations in the engine speed.
Examples of decouplers are disclosed in the United States Patent 6,083,130, issued to Mevissen et al. on July 4, 2000 and the United States Patent 5,139,463, issued to Bytzek et al.
on August 18, 1992.
It remains desirable to provide a decoupler that is easier to manufacture and has better durability over conventional de,coupler designs.
SUBSTITUTE SHEET (RULE 26) SLTNIMARY OF THE INVENTION
According to one aspect of the invention, a decoupler assembly is provided for transfernng torque between a shaft and a drive belt. The decoupler assembly includes a hub configured to be fixedly secured to the shaft. The hub includes a helical first slot formed therein. A earner is rotatably mounted on the hub. The carrier includes a helical second slot formed therein. A torsion spring extends between a hub end and a carrier end for transfernng torque between the hub and carrier, wherein the hub end is retained in the helical first slot to prevent relative movement between the hub end of the torsion spring and the hub and the carrier end is retained in the helical second slot to prevent relative movement between the earner end of the torsion spring and the earner. A pulley is rotatably coupled to the hub. The pulley includes an outer surface configured to frictionally engage with the drive belt. The pulley has an inner surface formed therein. A clutch spring is fixedly secured to the carrier and has a plurality of helical coils frictionally engaging with the inner surface of the pulley to selectively couple the hub and pulley. The torsion spring and the clutch spring are wound in opposite senses enabling the clutch spring to expand into gripping engagement with the inner surface during acceleration of the pulley relative to the hub and to contract out of gripping engagement with the inner surface during deceleration of the pulley relative to the hub.
BRIEF DESCRIPTION OF THE DRAWINGS
Advantages of the present invention will be readily appreciated as the same becomes better understood by reference to the following detailed description when considered in connection with the accompanying drawings wherein:
Figure 1 is a front view of an engine of an automotive vehicle incorporating a decoupler assembly according to one. aspect of the invention;
Figure 2 is an enlarged fragmentary sectional view of the decoupler assembly;
Figure 3 is a perspective view of a clutch spring in the decoupler assembly;
Figure 4 is a perspective view of a earner for carrying one end of the clutch spring in the decoupler assembly;
Figure 5 is a perspective view of the clutch spring assembled to the carrier;
Figure 6 is an exploded perspective view of the decoupler assembly according to a second embodiment of the invention;
Figure 7 is a cross sectional view of the decoupler assembly according to the second embodiment of the invention; and Figure 8 is a cross sectional view of the decoupler assembly according to a third embodiment of the invention.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT
Referring to the figures, an engine for an automotive vehicle is generally indicated at 10 in Figure 1. The engine 10 includes a crankshaft 12 driving an endless serpentine belt 14, as commonly known by those having ordinary skill in the a.rt. The engine 10 also includes a belt~driven accessory 16 driven by the belt 14. Described in greater detail below, a decoupler assembly 20 is operatively assembled between the belt 14 and the belt driven accessory 16 for automatically decoupling the belt driven accessory 16 from the. belt 14 when the belt 14 decelerates relative to the belt driven accessory 16 and allowing the speed of the belt 14 to oscillate relative to the belt driven accessory 16. Additionally, a detailed description of the structure and function of a decoupler assembly can be found in applicant's United States Patent 6,083,130, which issued on July 4, 2000 and is incorporated herein by reference in its entirety.
Referring to Figure 2, the decoupler assembly 20 includes a hub 22 having opposite.
first 24 and second 26 ends and a generally cylindrical body 28 extending axially therebetween. The body 28 includes opposite inner 30 and outer 32 surfaces extending between the first 24 and second 26 ends of the hub 22. The inner surface 30 includes a plurality of inner threads 33 adjacent the first end 24 for fixedly securing the hub 22 to a drive shaft 15 from the belt driven accessory 16. A reduced diameter portion 34 is formed in the first end 24. The reduced diameter portion 34 includes an outer mounting surface 36 having a smaller outer diameter than the body 28. An abutment surface 38 opposite the second end 26 extends generally radially between the outer mounting surface 36 and the body 28. An annular thrust washer 39 is seated on the outer mounting surface 36 adjacent the abutment surface 38.
A socket 40 is formed in the second end 26 for receiving a suitable tool therein for rotatably threading the hub 22 onto the drive shaft 15. An annular first flange 41 extends radially outwardly from the body 28 adjacent the second end 26. The first flange 41 includes an outer flange surface 42 having a larger outer diameter than the body 28. An annular surface 44 extends generally radially between the body 28 and the outer flange surface 42 opposite the second end 26. A generally helical first slot 46 is formed in the annular surface 44 defining a first locating surface 48 therein.
A generally cylindrical pulley 50 is rotatably journaled to the hub 22. More specifically, the pulley 50 extends between opposite first 52 and second 54 ends. The pulley 50 includes an inner surface 56 extending between the first 52 and second 54 ends. A ball ?0 bearing member 57 is coupled between the pulley 50 and the hub 22. The bearing member 57 includes an inner race 58 fixedly secured to a portion of the outer mounting surface 36 and an outer race 59 fixedly secured to a portion of the inner surface 56 adjacent the first end 52 of the pulley 50. A plurality of ball bearings 55 is rollingly engaged between the inner 58 and outer 59 races of the bearing member 57. A cylindrical bushing 60 is journal mounted between the pulley 50 and the first flange 41. The bushing 60 includes a sleeve wall 62 extending between a portion of the inner surface 56 adjacent the second end 54 and the outer flange surface 42 of the first flange 41. A bushing bushing flange 64 extends radially inwardly from the sleeve wall 62 and abuts the annular surface 44 in the first flange 41.
The pulley 50 includes an outer periphery 66 with a plurality of V-shaped grooves 68 formed therein for rollingly engaging and guiding the belt 14.
Referring to Figures 2-5, a one-way clutch assembly 70 is operatively coupled between the hub 22 and the pulley 50. The clutch assembly 70 includes a clutch spring 71 and a carrier 75. The clutch spring 71 includes a plurality of helical coils 72 extending between a bent or hooked proximal end 73 and an opposite distal end 74.
Preferably, the clutch spring 71 is formed from an uncoated, spring steel material and has a non-circular cross-section to improve frictional contact. Most preferably, the cross-section of clutch spring 71 is rectangular or square. The clutch spring 71 is press fitted into frictional engagement with the inner surface 56 of the pulley 50. Preferably, a lubricant similar or compatible with grease used in the ball bearing member 57 is applied to minimize wear between the clutch spring 71 and the inner surface 56 of the pulley 50.
The carrier 75 is rotatably mounted on the hub 22. The carrier 75 is generally ring shaped and extends axially between opposite first and second sides 76, 78. A
hooked slot 84 is formed in the second side 78 of the carrier 75 and is configured to retain the hooked proximal end 73 of the clutch spring 71. A generally helical second slot 86 is formed in the second side 78 of the carrier 75 defining a second locating surface 88 generally opposing the first locating surface 48 formed in the annular surface 44.
Referring to Figure 2, a helical torsion spring 90 extends between hub 92 and earner 94 ends. The torsion spring 90 is axially compressed between the first 48 and second 88 locating surfaces for transferring torque between the hub 22 and the carrier 75. More specifically, the hub end 92 of the torsion spring 90 is retained in the first slot 46 of the hub 22. Similarly, the earner end 94 of the torsion spring 90 is retained in the second slot 86 in the second side 78 of the earner 75. Axial forces due to the compression of the torsion spring 90 retains the first side 76 of the earner 75 in abutting engagement with the thrust washer 39.
The torsion spring 90 also allows relative movement between the earner 75 and the hub 22 to accommodate changes in the speed of the pulley 50 due to generally oscillating changes in the operating speed of the engine. The torsion spring 90 and the clutch spring 71 are coiled in opposite directions.
A cap 100 is fixedly assembled to a flange 102 formed in the pulley 50 for preventing contaminants from entering the decoupler assembly 20 and for retaining the lubricant within the decoupler assembly 20.
In operation, the engine 10 is started and the pulley 50 is accelerated and rotated in a driven direction by the belt 14 driven by the engine 10. Acceleration and rotation of the pulley 50 in the driven direction relative to the hub 22 creates friction between the inner surface 56 of the pulley 50 and preferably all of the coils 72 of the clutch spring 71. It should be appreciated that the clutch spring 71 will function even where at the onset at least one of the coils 72 of the clutch spring 71 is frictionally engaged with the inner surface 56 of the pulley 50. The clutch spring 71 is helically coiled such that the friction between the inner surface 56 of the pulley 50 and at least one of the coils 72 would cause the clutch spring 71 to expand radially outwardly toward and grip the inner surface 56 of the pulley 50. Continued rotation of the pulley 50 in the driven direction relative to the hub 22 would cause a generally exponential increase in the outwardly radial force applied by the coils 72 against the inner surface 56 until all of the coils 72 of the clutch spring 71 become fully brakingly engaged with the pulley 50. When the clutch spring 71 is fully engaged with the inner surface 56, the rotation of the pulley 50 is fully directed toward rotation of the drive shaft 15 of the belt driven accessory 16. Additionally, centrifugal forces help to retain the clutch spring 71 in braking engagement with the inner surface 56 of the pulley 50.
The rotational movement of the carrier 75 in the driven direction is transferred to the hub 22 by the torsional spring 90 such that generally the earner 75, thrust washer 39, hub 22, and the drive shaft 15 from the belt driven accessory 16 rotate together with the pulley 50.
Additionally, the torsional spring 90 resiliently allows relative movement between the carrier 75 and the hub 22 to accommodate oscillations in the speed of the pulley 50 due to corresponding oscillations in the operating speed of the engine 10.
When the pulley 50 decelerates, the hub 22 driven by the inertia associated with the rotating drive shaft 15 and the rotating mass within the belt driven accessory 16 will initially "overrun" or continue to rotate in the driven direction at a higher speed than the pulley 50.
More specifically, the higher rotational speed of the hub 22 relative to the pulley 50 causes the clutch spring 71 to contract radially relative to the inner surface 56 of the pulley 50. The braking engagement between the clutch spring 71 and the pulley 50 is relieved, thereby allowing overrunning of the hub '22 and drive shaft 15 from the belt driven accessory 16 relative to the pulley 50. The coils 72 may remain frictionally engaged with the inner surface 56 while the pulley 50 decelerates relative to the clutch assembly 70 and the hub 22. The coils 72 of the clutch spring 71 begin to brakingly reengage the inner surface 56 as the pulley 50 accelerates beyond the speed of the hub 22.
Referring to Figures 6 and 7, a second embodiment of the decoupler assembly 20' is shown, wherein elements of the alternative embodiment similar to those in the first embodiment are indicated by primed reference characters. The decoupler assembly 20' is assembled between an output or cranlahaft 106 of an engine and the belt 14' to allow the belt 14' to overrun the crankshaft 106. The decoupler assembly 20' includes a generally rinb shaped spring support 110. The slot 46' of the hub 22' has a generally U-shaped cross section for retaining the spring support 110 therein.
A first tab 112 extends outwardly from the spring support 110. A first notch 114 is formed in the hub end 92' of the torsion spring 90' for axially receiving the first tab 112 therein. Engagement between the first tab 112 and the first notch 114 prevents relative rotational movement of the hub end 92' of the torsion spring 90' relative to the spring support 110 and hub 22'. Similarly, a second tab 116 extends outwardly from the second locating surface 88' of the carne.r 75'. A second notch 118 is formed in the carrier end 94' of the torsion spring 90' for axially receiving the second tab 116 therein.
Engagement between the second tab 116 and the second notch 118 prevents relative rotational movement of the carrier end 94' of the torsion spring 90' relative to the carrier 75'.
The pulley 50' includes an outer periphery 120 for seating the belt 14' therein and an inner flange portion 122. The inner flange portion 122 has a generally U-shaped cross section defined by outer 124 and inner 126 pulley walls and a first connecting wall 12S
extending radially therebetween. The cawier 75' is retained between the outer 124 and inner 126 pulley walls and the first connecting wall 128 of the inner flange portion 122, such that the carrier 75' rotates with the pulley 50'. A second connecting wall 130 extends radially between the outer pulley wall 124 and the outer periphery 120.
The earner 75' includes a slot or split 132, which helps the carrier 75' to flex and accommodate loads associated with the rotation of the decoupler assembly 22'.
Referring to Figure 8, a third embodiment of the decoupler assembly 20" is shown, wherein the body 28" and first flange 41" of the hub 22" are fornled separately and fixedly connected in a subsequent assembly operation. The body 28" of the hub 22" is generally cylindrical and extends between the first 24" and second 26" ends. The first flange 41"
includes a mounting portion 140, which has a center bore 142 for receiving the outer flange surface 36" of the hub 22" therethrough. The first flange 41" includes a generally U-shaped cross section defined by an end wall 134 extending radially between generally parallel inner 136 and outer 138 flange walls. The spring support 110" is retained between the inner 136 and outer 138 flange walls and the end wall 134, such that the spring support 110" rotates with the first flange 41 ".
The outer periphery 120" and the inner flange portion 122" of the pulley 50"
are formed separately and fixedly connected in a subsequent assembly operation using any suitable method, such as welding. The generally U-shaped cross section of the inner flange portion 122" opens toward the first flange 41". The carrier 75" is retained between the outer 124" and inner 126" pulley walls and the first connecting wall 128", such that the carrier 75"
rotates with the pulley 50".
A ring plate 143 is mounted concentrically onto the outer mounting surface 36"
adjacent the abutment surface 38". A thrust washer 144 is disposed between the first flange 41" and the ring plate 143. The thrust washer 144 is axially spaced apart from the end wall 134 of the flange 41" for receiving the inner flange portion 122" of the pulley 50"
therebetween.
A torsional vibration damper 146, as known by those skilled in the art, is fixedly secured to the outer flange wall 138 of the first flange 41" for dampening vibrations experienced at the crankshaft 106 associated with the operations of the engine.
The invention has been described in an illustrative manner, and it is to be understood that the terminology, which has been used, is intended to be in the nature of words of description rather than of limitation. Many modification and variations of the present invention are possible in light of the above teachings. It is, therefore, to be understood that within the scope of the appended claims, the invention may be practiced other than as ~ specifically described.
Claims (29)
1. A decoupler assembly for transferring torque between a shaft and a drive belt, said decoupler assembly comprising:
a hub configured to be fixedly assembled to the shaft, said hub including a helical first slot formed therein;
a carrier rotatably mounted on said hub, said carrier including a helical second slot formed therein;
a torsion spring extending between a hub end and a carrier and for transferring torque between said hub and carrier, wherein said hub end is retained in said helical first slot to prevent relative movement between said hub end of said torsion spring and said hub and said carrier end is retained in said helical second slot to prevent relative movement between said carrier end of said torsion spring and said carrier.
a pulley rotatably coupled to said hub, said pulley having an outer periphery configured to frictionally engage with the drive belt, said pulley having an inner surface formed therein;
a clutch spring formed from an uncoated spring steel material fixedly secured to said carrier and having a plurality of helical coils frictionally engaging with said inner surface of said pulley to selectively couple said hub and pulley, said torsion spring and said clutch spring wound in opposite senses enabling said clutch spring to expand into gripping engagement with said inner surface during acceleration of said pulley relative to said hub and to contract out of gripping engagement with said inner surface during deceleration of said pulley relative to said hub.
a hub configured to be fixedly assembled to the shaft, said hub including a helical first slot formed therein;
a carrier rotatably mounted on said hub, said carrier including a helical second slot formed therein;
a torsion spring extending between a hub end and a carrier and for transferring torque between said hub and carrier, wherein said hub end is retained in said helical first slot to prevent relative movement between said hub end of said torsion spring and said hub and said carrier end is retained in said helical second slot to prevent relative movement between said carrier end of said torsion spring and said carrier.
a pulley rotatably coupled to said hub, said pulley having an outer periphery configured to frictionally engage with the drive belt, said pulley having an inner surface formed therein;
a clutch spring formed from an uncoated spring steel material fixedly secured to said carrier and having a plurality of helical coils frictionally engaging with said inner surface of said pulley to selectively couple said hub and pulley, said torsion spring and said clutch spring wound in opposite senses enabling said clutch spring to expand into gripping engagement with said inner surface during acceleration of said pulley relative to said hub and to contract out of gripping engagement with said inner surface during deceleration of said pulley relative to said hub.
2. A decoupler assembly as set forth in claim 1 wherein said hub includes a body extending axially between first and second ends.
3. A decoupler assembly as set forth in claim 2 wherein said hub includes a cylindrical outer surface extending between said first and second ends.
4. A decoupler assembly as set forth in claim 3 wherein said hub includes a first flange extending radially outwardly from said body to define an outer flange surface having a larger diameter than said body.
5. A decoupler assembly as set forth in claim 4 wherein said first flange includes an annular surface extending radially between said body and said outer flange surface.
6. A decoupler assembly as set forth in claim 5 wherein said helical first slot is formed in said annular surface for retaining therein said hub end of said torsion spring for preventing relative movement between said hub end of said torsion spring and said hub.
7. A decoupler assembly as set forth in claim 6 wherein said hub includes a reduced diameter portion having an outer mounting surface having a smaller diameter than said body of said hub.
8. A decoupler assembly as set forth is claim 7 wherein said hub includes an abutment surface extending radially between said body and said outer mounting surface.
9. A decoupler assembly as set forth in claim 8 wherein said carrier is ring shaped and extends axially between opposite first and second sides.
10. A decoupler assembly as set forth in claim 9 wherein said helical second slot is formed in one of said first and second sides of said carrier for retaining therein said carrier end of said torsion spring for preventing relative movement between said carrier end of said torsion spring and said carrier.
11. A decoupler assembly as set forth in claim 10 wherein clutch spring extends between a hooked proximal end and an opposite distal end.
12. A decoupler assembly as set forth in claim 11 wherein at least one of said first and second ends of said carrier includes a hooked slot for retaining therein said hooked proximal end of said clutch spring to prevent relative movement between said hooked proximal end of said clutch spring and said carrier.
13. A decoupler assembly as set forth in claim 12 wherein said clutch spring includes a non-circular cross-section to improve frictional engagement between said plurality of coils and said inner surface of said pulley.
14. A decoupler assembly as set forth in claim 13 including a bearing member operatively assembled between said pulley and acid hub for rotatably mounting said pulley on said hub.
15 A decoupler assembly as set forth in claim 14 wherein said decoupler assembly includes a first lubricant operatively associated with said bearing member for minimizing frictional wear therein and a second lubricant disposed between said clutch spring and said inner surface of the pulley for minimizing wear therebetween, said second lubricant being compatible with said first lubricant such that said the decoupler continues to function if said first lubricant is displaced from said bearing member and mixes with said second lubricant between said clutch spring and said inner surface.
16. A decoupler assembly as set forth in claim 15 wherein said bearing member includes a ball bearing assembly having an inner race engaging said hub and an outer race engaging said pulley.
17. A decoupler assembly as set forth in claim 16 including a thrust washer seated en said eater mounting surface of said reduced diameter portion for axially compressing said torsion spring between said carrier and said hub.
18. A decoupler assembly as set forth in claim 17 wherein said inner race of said ball bearing assembly is press fit onto said outer mounting surface of said reduced diameter portion to retain said thrust washer against said abutment surface, whereby said axial compression of said torsion spring is maintained.
19. A decoupler assembly as set forth in claim 18 wherein said carrier includes a split to allow said carrier to flex and accommodate loads associated with rotation of said decoupler assembly.
20. A decoupler assembly for transferring torque between an engine driven crankshaft shaft and a drive belt, said decoupler assembly comprising:
a hub configured to be fixedly assembled to the crankshaft;
a spring support fixedly secured to said hub, said spring support having a first tab extending outwardly therefrom;
a carrier rotatably mounted on said hub, said carrier having a second tab extending outwardly therefrom;
a torsion spring extending between a hub end and a carrier end for transferring torque between said spring support and carrier, wherein said hub end includes a first notch engaged with said first tab to prevent relative rotation between said hub end of said torsion spring and said spring support and said carrier end includes a second notch engaged with said second tab to prevent relative rotation between said carrier end of said torsion spring and said carrier.
a pulley rotatably coupled to said hub, said pulley having an outer periphery configured in frictionally engage with the drive belt, said pulley having an inner surface formed therein;
a clutch spring fixedly secured to said carrier and having a plurality of helical coils frictionally engaging with said inner surface of said pulley to selectively couple said hub and pulley, said torsion spring and said clutch spring wound in opposite senses enabling said clutch spring to expand into gripping engagement with said inner surface during acceleration of said hub relative to said pulley sad to contract out of gripping engagement with said inner surface during deceleration of said hub relative to said pulley.
a hub configured to be fixedly assembled to the crankshaft;
a spring support fixedly secured to said hub, said spring support having a first tab extending outwardly therefrom;
a carrier rotatably mounted on said hub, said carrier having a second tab extending outwardly therefrom;
a torsion spring extending between a hub end and a carrier end for transferring torque between said spring support and carrier, wherein said hub end includes a first notch engaged with said first tab to prevent relative rotation between said hub end of said torsion spring and said spring support and said carrier end includes a second notch engaged with said second tab to prevent relative rotation between said carrier end of said torsion spring and said carrier.
a pulley rotatably coupled to said hub, said pulley having an outer periphery configured in frictionally engage with the drive belt, said pulley having an inner surface formed therein;
a clutch spring fixedly secured to said carrier and having a plurality of helical coils frictionally engaging with said inner surface of said pulley to selectively couple said hub and pulley, said torsion spring and said clutch spring wound in opposite senses enabling said clutch spring to expand into gripping engagement with said inner surface during acceleration of said hub relative to said pulley sad to contract out of gripping engagement with said inner surface during deceleration of said hub relative to said pulley.
21. A decoupler assembly as set forth in claim 20 wherein said hub includes a body extending between first and second ends.
22. A decoupler assembly as set forth in claim 21 wherein said hub includes a reduced diameter portion defining an outer mounting surface having an outer diameter smaller than said body.
23. A decoupler assembly as set forth in claim 22 wherein said hub includes an abutment surface extending between said outer mounting surface and said body.
24. A decoupler assembly as set forth in claim 23 including a flange having a mounting portion configured for fixedly mounting said flange onto said outer mounting surface.
25. A decoupler assembly as set forth in claim 24 wherein said flange includes a U-shaped truss section defined by an end wall extending between inner and outer flange walls.
26. A decoupler assembly as set forth in claim 25 wherein said carrier is retained between said inner and outer flange walls and said end wall, such that said carrier and said crutch spring rotate together with said flange.
27. A decoupler assembly as set forth in claim 26 wherein said pulley includes as inner flange portion having a U-shaped cross section defined by a connecting wall extending between outer and inner pulley walls.
28. A decoupler assembly as set forth is claim 27 wherein said spring support is retained between said outer and inner pulley walls and said connecting wall, such that said spring support rotates with said pulley.
29. A decoupler assembly as set forth in claim 28 including a thrust washer disposed between said mounting portion of said flange and said abutment surface for continuously biasing said first and second tabs of said spring support and carrier toward engagement with said first and second notches of said hub and carrier ends of said torsion spring, respectively.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US39897902P | 2002-07-26 | 2002-07-26 | |
| US60/398,979 | 2002-07-26 | ||
| PCT/CA2003/001168 WO2004011818A1 (en) | 2002-07-26 | 2003-07-25 | Overrunning alternator decoupler pulley with bare wire spring and grease lubrication |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CA2491230A1 true CA2491230A1 (en) | 2004-02-05 |
| CA2491230C CA2491230C (en) | 2013-06-25 |
Family
ID=31188528
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA2491230A Expired - Lifetime CA2491230C (en) | 2002-07-26 | 2003-07-25 | Overrunning alternator decoupler pulley with bare wire spring and grease lubrication |
Country Status (14)
| Country | Link |
|---|---|
| US (2) | US7618337B2 (en) |
| EP (2) | EP1534972B1 (en) |
| JP (2) | JP4628100B2 (en) |
| KR (3) | KR101187150B1 (en) |
| CN (1) | CN100335808C (en) |
| AT (2) | ATE397164T1 (en) |
| AU (1) | AU2003250703A1 (en) |
| BR (1) | BRPI0312646B1 (en) |
| CA (1) | CA2491230C (en) |
| DE (2) | DE60318721T2 (en) |
| ES (2) | ES2298586T3 (en) |
| MX (1) | MXPA04012817A (en) |
| RU (1) | RU2005102818A (en) |
| WO (1) | WO2004011818A1 (en) |
Families Citing this family (135)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7153227B2 (en) * | 2002-04-18 | 2006-12-26 | Litens Automotive | Isolator for alternator pulley |
| ATE397164T1 (en) * | 2002-07-26 | 2008-06-15 | Litens Automotive | CUTTING DISC FOR CONTINUOUS THREE-PHASE GENERATOR WITH BARE WIRE SPRING AND GREASE LUBRICATION |
| BRPI0407189B1 (en) * | 2003-02-04 | 2016-03-08 | Litens Automotive | uncoupler |
| PL2273144T3 (en) * | 2003-09-22 | 2013-04-30 | Litens Automotive Inc | Crankshaft decoupler |
| DE602004028153D1 (en) | 2003-12-09 | 2010-08-26 | Litens Automotive Inc | SPRING LEVER LIMITER FOR OVERFLOW COUPLER |
| JP5026687B2 (en) * | 2004-12-02 | 2012-09-12 | 三ツ星ベルト株式会社 | Pulley structure |
| US7766774B2 (en) * | 2005-02-03 | 2010-08-03 | Litens Automotive Partnership | Torque limited decoupler |
| DE102005055034B3 (en) * | 2005-09-01 | 2007-02-08 | Muhr Und Bender Kg | Torsion oscillation damper/decoupler, e.g. for a motor crankshaft or camshaft, has a hub and disk rim rotating within each other together with coiled wire springs |
| FR2891039B1 (en) * | 2005-09-19 | 2009-05-22 | Hutchinson Sa | POWER TRANSMISSION PULLEY |
| DE602005016575D1 (en) * | 2005-11-18 | 2009-10-22 | Ford Global Tech Llc | Combustion engine arrangement |
| DE102005062318A1 (en) * | 2005-12-24 | 2007-07-12 | Schaeffler Kg | Traction drive for an internal combustion engine |
| US7878315B2 (en) * | 2006-04-14 | 2011-02-01 | Ntn Corporation | Spring clutch |
| WO2007121582A1 (en) | 2006-04-26 | 2007-11-01 | Litens Automotive Partnership | One-way isolator for high torque devices |
| WO2008004258A1 (en) * | 2006-07-07 | 2008-01-10 | Dayco Europe S.R.L. | Pulley assembly |
| DE112007002873A5 (en) * | 2006-12-11 | 2009-10-08 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Decoupler assembly |
| US8632431B2 (en) * | 2006-12-11 | 2014-01-21 | Schaeffler Technologies AG & Co. KG | Drive wheel of an auxiliary unit belt drive of an internal combustion engine |
| CN101200075B (en) * | 2006-12-17 | 2011-12-21 | 软控股份有限公司 | Protection device of ultrasonic cutter and method thereof |
| DE102007001818A1 (en) | 2007-01-12 | 2008-07-17 | Schaeffler Kg | Belt pulley rotary speed and/or torque variation reducing device for belt drive of internal combustion engine of motor vehicle, has springs with middle section clamped by dogs, where number of dogs corresponds to number of springs |
| JP2009008247A (en) * | 2007-02-28 | 2009-01-15 | Ntn Corp | Rotational direction switching clutch unit |
| JP4816529B2 (en) * | 2007-03-22 | 2011-11-16 | 株式会社ジェイテクト | Pulley unit |
| US7878913B2 (en) * | 2007-10-26 | 2011-02-01 | Ford Global Technologies, Llc | Decoupling torsional disturbance in a vehicle powertrain |
| US20090197719A1 (en) * | 2008-01-31 | 2009-08-06 | Imtiaz Ali | Torsional decoupler |
| US8192312B2 (en) * | 2008-01-31 | 2012-06-05 | The Gates Corporation | Isolator with damping |
| US7892124B2 (en) * | 2008-03-07 | 2011-02-22 | The Gates Corporation | Decoupling isolator |
| US8216113B2 (en) | 2008-05-27 | 2012-07-10 | Litens Automotive Partnership | Engine powered device having accessory drive and reversing motor for selectively starting engine and powering accessory drive |
| US8272982B2 (en) | 2008-07-09 | 2012-09-25 | Ct Drives, Llc | Cam damped pulley for rotary devices |
| US8888619B2 (en) * | 2008-10-27 | 2014-11-18 | Litens Automotive Partnership | Over-running decoupler with torque limiter |
| KR101749471B1 (en) * | 2008-11-17 | 2017-06-20 | 리텐스 오토모티브 파트너쉽 | A helical coil clutch assembly comprising an actuator to effect engagement of helical coil clutch with a clutch surface |
| DE102008059572A1 (en) * | 2008-11-28 | 2010-06-02 | Schaeffler Kg | Shaft-hub connection between a pulley and a generator shaft and belt-driven starter generator with such a shaft-hub connection |
| US8789670B2 (en) | 2009-03-03 | 2014-07-29 | Litens Automotive Partnership | Decoupler featuring helical wrap clutch spring and coil damper springs |
| CN102439284B (en) * | 2009-05-15 | 2014-07-30 | 利滕斯汽车合伙公司 | Engine starter |
| JP5227269B2 (en) | 2009-06-19 | 2013-07-03 | 三ツ星ベルト株式会社 | Power transmission mechanism |
| US9068608B2 (en) * | 2009-09-17 | 2015-06-30 | Gates Corporation | Isolator decoupler |
| DE102009052611B4 (en) | 2009-11-10 | 2018-06-07 | Schaeffler Technologies AG & Co. KG | Pulley arrangement |
| AU2010325793B2 (en) | 2009-12-04 | 2015-03-12 | Uber Technologies, Inc. | System and method for arranging transport amongst parties through use of mobile devices |
| DE102010006416A1 (en) * | 2010-02-01 | 2011-08-04 | Schaeffler Technologies GmbH & Co. KG, 91074 | Drive plate with integrated freewheel |
| US8419574B2 (en) * | 2010-04-06 | 2013-04-16 | The Gates Corporation | Isolator |
| US8602928B2 (en) * | 2010-04-15 | 2013-12-10 | Gates Corporation | Isolator |
| FR2959547B1 (en) | 2010-04-30 | 2012-06-08 | Hutchinson | DECOUPLING PULLEY. |
| CN102906441B (en) * | 2010-05-25 | 2016-11-09 | 利滕斯汽车合伙公司 | There is between hub and belt wheel the decoupler assembly of sliding interface |
| CA2802114A1 (en) | 2010-06-25 | 2011-12-29 | Litens Automotive Partnership | Overrunning decoupler |
| EP2585728B1 (en) | 2010-06-25 | 2019-09-18 | Litens Automotive Partnership | Decoupler with integrated torsional vibration damper |
| EP2585727A4 (en) | 2010-06-25 | 2018-03-28 | Litens Automotive Partnership | Isolation pulley with overrunning and vibration damping capabilities |
| CN101936348B (en) * | 2010-09-07 | 2012-07-11 | 江苏南方轴承股份有限公司 | Belt pulley of over-travel alternating current generator decoupler |
| WO2012061930A1 (en) * | 2010-11-09 | 2012-05-18 | Litens Automotive Partnership | Decoupler assembly having limited overrunning capability |
| CA2814551A1 (en) * | 2010-11-14 | 2012-05-18 | Litens Automotive Partnership | Decoupler with tuned damping and methods associated therewith |
| CN103459875B (en) | 2011-01-14 | 2016-08-17 | 利滕斯汽车合伙公司 | There is the arrangement of clutch of thrust ring |
| US8506434B2 (en) | 2011-01-24 | 2013-08-13 | The Gates Corporation | Isolating decoupler |
| ITTO20110300A1 (en) * | 2011-04-01 | 2012-10-02 | Dayco Europe Srl | DETACHABLE PULLEY FOR A BELT OR CHAIN TRANSMISSION |
| US9284994B2 (en) | 2011-04-04 | 2016-03-15 | Litens Automotive Partnership | Clutch mechanism and decoupler device with same |
| US9169904B2 (en) | 2011-04-11 | 2015-10-27 | Litens Automotive Partnership | Multi-speed drive for transferring power to a load |
| US20120322592A1 (en) * | 2011-04-11 | 2012-12-20 | Zen Sa Industria Metalurgica | Overrunning pulley with elastomer torsional damping system |
| CN102758908A (en) * | 2011-04-27 | 2012-10-31 | 武汉集信传动技术有限公司 | Spring extension type overrunning belt pulley structure |
| EP3323658B1 (en) | 2011-05-13 | 2021-11-24 | Litens Automotive Partnership | Intelligent belt drive system and method |
| WO2013131166A1 (en) * | 2011-08-08 | 2013-09-12 | Litens Automotive Partnership | Decoupler assembly |
| CN102305251B (en) * | 2011-08-25 | 2014-07-23 | 江苏南方轴承股份有限公司 | Composite retainer for decoupler pulley and decoupler pulley |
| US9464697B2 (en) | 2011-09-05 | 2016-10-11 | Litens Automotive Partnership | Intelligent belt drive system and method |
| CN102359508B (en) * | 2011-09-06 | 2015-10-14 | 江苏南方轴承股份有限公司 | Coupling tuning pulley |
| WO2013034090A1 (en) * | 2011-09-06 | 2013-03-14 | 江苏南方轴承股份有限公司 | Coupling tuning belt pulley |
| KR101970377B1 (en) | 2011-10-06 | 2019-04-18 | 리텐스 오토모티브 파트너쉽 | Clutched driven device and associated clutch mechanism |
| US8813928B2 (en) * | 2011-10-14 | 2014-08-26 | The Gates Corporation | Alternator isolating decoupler |
| CN103649595A (en) * | 2011-11-25 | 2014-03-19 | 日本精工株式会社 | Rotating machine with pulley and built-in one-way clutch |
| US8813932B2 (en) * | 2012-03-08 | 2014-08-26 | The Gates Corporation | Isolator decoupler |
| CN104254703B (en) | 2012-04-10 | 2017-02-08 | 利滕斯汽车合伙公司 | Clutch assembly |
| US9441681B2 (en) | 2012-04-18 | 2016-09-13 | Litens Automotive Partnership | Power transmitting device with overrunning decoupler |
| WO2013159181A1 (en) * | 2012-04-28 | 2013-10-31 | Litens Automotive Partnership | Adjustable tensioner |
| US8888622B2 (en) | 2012-06-04 | 2014-11-18 | The Gates Corporation | Isolator decoupler |
| KR20150029645A (en) * | 2012-06-20 | 2015-03-18 | 데이코 아이피 홀딩스 엘엘시 | Accessory drive decoupler |
| WO2014022912A1 (en) | 2012-08-07 | 2014-02-13 | Litens Automotive Partnership | Decoupler carrier with balanced forces |
| BR102012022803B1 (en) | 2012-09-10 | 2017-05-02 | Zen S/A Indústria Metalúrgica | decoupler with freewheel system and vibration damping |
| US11236812B2 (en) | 2012-09-10 | 2022-02-01 | Zen S/A Industria Metalurgica | Decoupler with one-way clutch and fail-safe system |
| US20150285312A1 (en) * | 2012-10-12 | 2015-10-08 | Litens Automotive Partnership | Isolator for use with mgu that is used to assist or start engine through and endless drive member |
| US9140319B2 (en) | 2012-11-20 | 2015-09-22 | Litens Automotive Partnership | Decoupler with concentric clutching members |
| WO2014113862A1 (en) | 2013-01-25 | 2014-07-31 | Litens Automotive Partnership | Clutched device with wrap spring clutch with overrun locking member |
| US9182028B2 (en) | 2013-02-08 | 2015-11-10 | Motorcar Parts Of America, Inc. | Torsional impact damping and decoupling pulley |
| US9556918B2 (en) | 2013-04-10 | 2017-01-31 | Litens Automotive Partnership | Clutch assembly |
| US9611928B2 (en) * | 2013-06-13 | 2017-04-04 | Zhimin Li | Unidirectional coupling damping pulley |
| ITTO20130677A1 (en) | 2013-08-06 | 2015-02-07 | Dayco Europe Srl | FILTERING PULLEY FOR A BELT DRIVE |
| KR101500138B1 (en) * | 2013-09-10 | 2015-03-06 | 현대자동차주식회사 | Decoupling device of crank pully |
| WO2015070329A1 (en) | 2013-11-14 | 2015-05-21 | Litens Automotive Partnership | Decoupler with overrunning and belt-start capability with simplified construction |
| JP6256013B2 (en) * | 2014-01-09 | 2018-01-10 | 株式会社ジェイテクト | Pulley unit |
| WO2015103697A1 (en) | 2014-01-10 | 2015-07-16 | Litens Automotive Partnership | Decoupler with overrunning and belt-start capability |
| US9097297B1 (en) * | 2014-01-17 | 2015-08-04 | Gates Corporation | Hydraulic isolator decoupler |
| US9033832B1 (en) | 2014-01-23 | 2015-05-19 | Gates Corporation | Isolating decoupler |
| US9206892B2 (en) * | 2014-04-08 | 2015-12-08 | Gates Corporation | Isolating decoupler |
| US9291217B2 (en) | 2014-04-08 | 2016-03-22 | Dayco Ip Holdings, Llc | Pulley assembly with radially oriented decoupling mechanism |
| US9476497B2 (en) * | 2014-04-23 | 2016-10-25 | Ningbo Yangtong Automobile Parts Co., Ltd | Unidirectional clutch decoupling device for transferring torque between belt wheel and shaft |
| WO2015172967A1 (en) * | 2014-05-16 | 2015-11-19 | Rollax Gmbh & Co. Kg | Device for the transmission of a torque with torsional vibration damping |
| EP2977631B1 (en) * | 2014-07-14 | 2018-06-13 | Victory Industrial Corporation | Pulley for alternator |
| TWI555932B (en) | 2014-07-14 | 2016-11-01 | 勝利工業股份有限公司 | Pulley for an alternator |
| TWI551795B (en) | 2014-07-14 | 2016-10-01 | 勝利工業股份有限公司 | Pulley for an alternator |
| TWI551794B (en) | 2014-07-14 | 2016-10-01 | 勝利工業股份有限公司 | Pulley for an alternator |
| US9341254B2 (en) * | 2014-08-08 | 2016-05-17 | Gates Corporation | Isolating pulley |
| US9546709B2 (en) * | 2014-09-10 | 2017-01-17 | Gates Corporation | Crankshaft isolating pulley |
| KR101610110B1 (en) * | 2014-09-30 | 2016-04-08 | 현대자동차 주식회사 | Alternator damper pulley for vehicle |
| DE102014223228B3 (en) * | 2014-11-13 | 2016-04-21 | Schaeffler Technologies AG & Co. KG | Pulley arrangement |
| DE102014117543A1 (en) * | 2014-11-28 | 2016-06-16 | Trelleborgvibracoustic Gmbh | Vibration damping device |
| BR102015001454B1 (en) | 2015-01-22 | 2022-06-28 | Fiat Automóveis Ltda | SYSTEM AND METHOD FOR SELECTIVE ELECTROMECHANICAL COUPLING AND/OR DECOUPING OF AUTOMOTIVE ALTERNATOR |
| DE102015202043A1 (en) * | 2015-02-05 | 2016-08-11 | Schaeffler Technologies AG & Co. KG | decoupler |
| DE102015202531B3 (en) * | 2015-02-12 | 2015-12-17 | Schaeffler Technologies AG & Co. KG | Riemenscheibenentkoppler |
| US9291253B1 (en) | 2015-03-24 | 2016-03-22 | Gates Corporation | Isolating decoupler |
| US9784357B2 (en) * | 2015-04-27 | 2017-10-10 | Ningbo Yangtong Automobile Parts Co., Ltd. | Overrunning alternator damping pulley |
| US10024415B2 (en) | 2015-11-02 | 2018-07-17 | Gates Corporation | Isolating decoupler |
| DE102015224608B4 (en) * | 2015-12-08 | 2021-02-04 | Schaeffler Technologies AG & Co. KG | Pulley decoupler |
| JP7231199B2 (en) * | 2016-02-11 | 2023-03-01 | セデマック メカトロニクス プライベート リミテッド | Method and system for crank starting an internal combustion engine |
| US10087994B2 (en) * | 2016-04-19 | 2018-10-02 | Gates Corporation | Isolating decoupler |
| US9797469B1 (en) * | 2016-05-13 | 2017-10-24 | Gates Corporation | Isolating decoupler |
| DE102016211141B4 (en) * | 2016-06-22 | 2021-04-22 | Schaeffler Technologies AG & Co. KG | Pulley decoupler |
| DE102016211558B4 (en) * | 2016-06-28 | 2019-01-31 | Schaeffler Technologies AG & Co. KG | Riemenscheibenentkoppler |
| FR3053394B1 (en) * | 2016-06-30 | 2019-08-09 | Hutchinson | DECOUPLING PULLEY WITH DEPARTURE CLUTCH |
| DE102016216274B4 (en) * | 2016-08-30 | 2018-08-02 | Schaeffler Technologies AG & Co. KG | Pulley decoupler with double hub |
| FR3058768B1 (en) * | 2016-11-15 | 2020-02-21 | Hutchinson | DECOUPLING PULLEY |
| US11274739B2 (en) | 2017-03-30 | 2022-03-15 | Mitsuboshi Belting Ltd. | Pulley structure and method for manufacturing pulley structure |
| JP6731433B2 (en) * | 2017-03-30 | 2020-07-29 | 三ツ星ベルト株式会社 | Pulley structure and method for manufacturing pulley structure |
| CN109386570A (en) * | 2017-08-11 | 2019-02-26 | 宁波市洋通汽车配件有限公司 | A kind of unidirectional vibration damping decoupler |
| US10520039B2 (en) | 2017-08-28 | 2019-12-31 | Gates Corporation | Isolating decoupler |
| WO2019046957A1 (en) | 2017-09-07 | 2019-03-14 | Litens Automotive Partnership | Single spring, torsionally compliant, overruning decoupler |
| CN107939907A (en) * | 2017-12-14 | 2018-04-20 | 龙岩阿赛特汽车零部件制造有限公司 | Spinning automobile crane vibration damping wheel |
| WO2019113658A1 (en) * | 2017-12-15 | 2019-06-20 | Zen S/A Indústria Metalúrgica | Decoupler with one way clutch and fail-safe system |
| FR3076335B1 (en) | 2018-01-04 | 2019-11-22 | Valeo Equipements Electriques Moteur | IMPROVED FRICTION IMPACT LIMITING PULLEY ASSEMBLY |
| FR3076333B1 (en) * | 2018-01-04 | 2020-08-14 | Valeo Equip Electr Moteur | IMPROVED SHOCK LIMITATION CLUTCH PULLEY ASSEMBLY |
| FR3076334B1 (en) * | 2018-01-04 | 2019-11-29 | Valeo Equipements Electriques Moteur | CLUTCH PULLEY ASSEMBLY WITH IMPROVED IMPACT LIMITING |
| FR3076332A1 (en) * | 2018-01-04 | 2019-07-05 | Valeo Equipements Electriques Moteur | PULLEY ASSEMBLY WITH IMPROVED VOLTAGE SPRING COMPRESSION LIMITATION ENHANCEMENT |
| KR102441083B1 (en) * | 2018-03-08 | 2022-09-06 | 현대자동차주식회사 | Damper pulley for crankshaft |
| DE102018109075A1 (en) | 2018-04-17 | 2019-10-17 | Schaeffler Technologies AG & Co. KG | Riemenscheibenentkoppler |
| US11028884B2 (en) * | 2018-07-20 | 2021-06-08 | Gates Corporation | Isolating decoupler |
| US11549558B2 (en) | 2018-08-01 | 2023-01-10 | Gates Corporation | Isolator decoupler |
| EP3948002B1 (en) | 2019-03-26 | 2024-04-03 | Litens Automotive Partnership | Rotary device with clutch with time-based slip and method of providing time-based slip for a rotary device |
| DE102019113443B4 (en) * | 2019-05-21 | 2021-02-11 | Schaeffler Technologies AG & Co. KG | Belt pulley decoupler with axial toothing on both sides as well as ancillary unit drive |
| FR3100852B1 (en) * | 2019-09-18 | 2021-09-03 | Hutchinson | Improved drive decoupling pulley |
| DE102019126867B4 (en) * | 2019-10-07 | 2021-04-22 | Schaeffler Technologies AG & Co. KG | Pulley decoupler |
| US11421642B2 (en) * | 2020-03-23 | 2022-08-23 | Ford Global Technologies, Llc | Flexible membrane isolator |
| DE102020118374B4 (en) | 2020-07-13 | 2022-01-27 | Schaeffler Technologies AG & Co. KG | Pulley decoupler |
| DE102020127092A1 (en) * | 2020-09-08 | 2022-03-10 | Schaeffler Technologies AG & Co. KG | Pulley decoupler with a support plate of a vibration absorber connected to a hub component |
| DE102022101636A1 (en) | 2022-01-25 | 2023-07-27 | Schaeffler Technologies AG & Co. KG | Decoupler and ancillary unit belt drive of an internal combustion engine with such a decoupler |
Family Cites Families (35)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| USRE25229E (en) | 1962-08-21 | Spring clutch mechanisms | ||
| US773320A (en) * | 1903-09-21 | 1904-10-25 | Charles L Haase Jr | Yielding shaft. |
| US2396985A (en) | 1945-03-10 | 1946-03-19 | Clark Equipment Co | Clutch mechanism |
| US2633953A (en) | 1948-11-09 | 1953-04-07 | Marquette Metal Products Co | Spring clutch mechanism |
| US2551739A (en) | 1950-02-03 | 1951-05-08 | Marquette Metal Products Co | Spring clutch and energizing means |
| US2794524A (en) | 1954-09-01 | 1957-06-04 | Curtiss Wright Corp | Spring clutch mechanisms |
| US2968380A (en) | 1957-01-30 | 1961-01-17 | Curtiss Wright Corp | Spring clutch mechanisms |
| US2829748A (en) | 1957-01-30 | 1958-04-08 | Curtiss Wright Corp | Spring clutch mechanisms |
| US2866349A (en) | 1957-05-27 | 1958-12-30 | Heckethorn Mfg & Supply Co | Variable speed drives for automotive generators |
| US2885896A (en) | 1957-11-25 | 1959-05-12 | Curtiss Wright Corp | Plural speed driving mechanisms |
| US3059493A (en) | 1959-06-08 | 1962-10-23 | Gen Motors Corp | Drive systems |
| US3242696A (en) * | 1963-10-29 | 1966-03-29 | Kaplan Joseph | Multiple spring slip element |
| US3298486A (en) | 1965-01-28 | 1967-01-17 | Curtiss Wright Corp | Spring clutch mechanism |
| US3618730A (en) | 1969-12-12 | 1971-11-09 | Vari Typer Corp | Torque-limiting clutch |
| JPS57186627A (en) | 1981-05-12 | 1982-11-17 | Matsushita Electric Ind Co Ltd | Spring clutch |
| JPS59183547U (en) * | 1983-05-24 | 1984-12-06 | 本田技研工業株式会社 | Clutch mechanism of power transmission device |
| US5156573A (en) * | 1991-06-05 | 1992-10-20 | Litens Automotive Partnership | Serpentine drive with coil spring-one-way clutch alternator connection |
| US5139463A (en) | 1991-06-05 | 1992-08-18 | Litens Automotive Partnership | Serpentine drive with coil spring alternator connection |
| JP3178932B2 (en) * | 1993-03-02 | 2001-06-25 | 富士通株式会社 | Semiconductor integrated circuit device |
| US5437205A (en) * | 1994-01-14 | 1995-08-01 | Tseng; Sheng-Tsai | Wrap spring clutches type transmission system |
| US5598913A (en) | 1995-06-07 | 1997-02-04 | Ntn Corporation | One-way over-running clutch pulley |
| EP0825363B1 (en) | 1996-08-22 | 2001-10-10 | Koyo Seiko Co., Ltd. | Pulley |
| KR100532892B1 (en) | 1997-05-07 | 2005-12-05 | 리텐스 오토모티브 파트너쉽 | Serpentine drive system with improved over-running alternator decoupler |
| DE19802251B4 (en) * | 1998-01-22 | 2005-06-16 | Zf Sachs Ag | wrap spring |
| JP2003535281A (en) | 2000-05-31 | 2003-11-25 | ラッセル モナハン | Overrunning clutch pulley with floating spring member |
| US6394247B1 (en) | 2000-05-31 | 2002-05-28 | Ntn Corporation | Complaint one way over-running clutch pulley |
| US7052420B2 (en) * | 2000-05-31 | 2006-05-30 | Ntn Corporation | Over-running clutch pulley with coating material |
| US7191880B2 (en) * | 2000-05-31 | 2007-03-20 | Ntn Corporation | Over-running clutch pulley with increased surface microhardness |
| US6394248B1 (en) | 2000-05-31 | 2002-05-28 | Ntn Corporation | Compression spring complaint one-way over-running clutch pulley |
| DE60121906T2 (en) * | 2000-10-26 | 2007-02-15 | Jtekt Corp., Osaka | Fastening arrangement of a belt pulley |
| US6637570B2 (en) | 2001-11-29 | 2003-10-28 | Ntn Corporation | Over-running clutch pulley with composite sealing member |
| US7153227B2 (en) * | 2002-04-18 | 2006-12-26 | Litens Automotive | Isolator for alternator pulley |
| US6761656B2 (en) * | 2002-05-31 | 2004-07-13 | Ntn Corporation | Over-running clutch pulley with clutch cartridge |
| ATE397164T1 (en) | 2002-07-26 | 2008-06-15 | Litens Automotive | CUTTING DISC FOR CONTINUOUS THREE-PHASE GENERATOR WITH BARE WIRE SPRING AND GREASE LUBRICATION |
| US7613874B2 (en) * | 2004-10-14 | 2009-11-03 | Lg Electronics, Inc. | Recording medium, and a method and apparatus for overwriting data in the same |
-
2003
- 2003-07-25 AT AT07001751T patent/ATE397164T1/en not_active IP Right Cessation
- 2003-07-25 EP EP03771041A patent/EP1534972B1/en not_active Expired - Lifetime
- 2003-07-25 ES ES03771041T patent/ES2298586T3/en not_active Expired - Lifetime
- 2003-07-25 EP EP07001751A patent/EP1772644B1/en not_active Expired - Lifetime
- 2003-07-25 AT AT03771041T patent/ATE384205T1/en not_active IP Right Cessation
- 2003-07-25 CN CNB038165430A patent/CN100335808C/en not_active Expired - Lifetime
- 2003-07-25 CA CA2491230A patent/CA2491230C/en not_active Expired - Lifetime
- 2003-07-25 KR KR1020107029372A patent/KR101187150B1/en active IP Right Grant
- 2003-07-25 WO PCT/CA2003/001168 patent/WO2004011818A1/en active IP Right Grant
- 2003-07-25 DE DE60318721T patent/DE60318721T2/en not_active Expired - Lifetime
- 2003-07-25 JP JP2004523711A patent/JP4628100B2/en not_active Expired - Lifetime
- 2003-07-25 RU RU2005102818/11A patent/RU2005102818A/en not_active Application Discontinuation
- 2003-07-25 KR KR1020057001333A patent/KR101052664B1/en active IP Right Grant
- 2003-07-25 DE DE60321409T patent/DE60321409D1/en not_active Expired - Lifetime
- 2003-07-25 AU AU2003250703A patent/AU2003250703A1/en not_active Abandoned
- 2003-07-25 KR KR1020127019650A patent/KR20120099786A/en not_active Application Discontinuation
- 2003-07-25 ES ES07001751T patent/ES2306440T3/en not_active Expired - Lifetime
- 2003-07-25 US US10/519,591 patent/US7618337B2/en active Active
- 2003-07-25 BR BRPI0312646A patent/BRPI0312646B1/en not_active IP Right Cessation
- 2003-07-25 MX MXPA04012817A patent/MXPA04012817A/en active IP Right Grant
-
2009
- 2009-03-12 US US12/402,819 patent/US20090176608A1/en not_active Abandoned
-
2010
- 2010-09-10 JP JP2010203060A patent/JP5620763B2/en not_active Expired - Lifetime
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| MXPA04012817A (en) | 2005-03-31 |
| DE60321409D1 (en) | 2008-07-10 |
| DE60318721T2 (en) | 2008-06-05 |
| US20090176608A1 (en) | 2009-07-09 |
| JP2005533980A (en) | 2005-11-10 |
| ATE397164T1 (en) | 2008-06-15 |
| DE60318721D1 (en) | 2008-03-06 |
| EP1772644A1 (en) | 2007-04-11 |
| CA2491230C (en) | 2013-06-25 |
| KR101052664B1 (en) | 2011-07-28 |
| WO2004011818A1 (en) | 2004-02-05 |
| US7618337B2 (en) | 2009-11-17 |
| KR101187150B1 (en) | 2012-09-28 |
| EP1534972B1 (en) | 2008-01-16 |
| BRPI0312646B1 (en) | 2015-10-27 |
| EP1772644B1 (en) | 2008-05-28 |
| EP1534972A1 (en) | 2005-06-01 |
| BR0312646A (en) | 2005-04-26 |
| AU2003250703A1 (en) | 2004-02-16 |
| CN1668859A (en) | 2005-09-14 |
| ES2298586T3 (en) | 2008-05-16 |
| KR20110014670A (en) | 2011-02-11 |
| ATE384205T1 (en) | 2008-02-15 |
| JP5620763B2 (en) | 2014-11-05 |
| KR20050039832A (en) | 2005-04-29 |
| ES2306440T3 (en) | 2008-11-01 |
| US20050250607A1 (en) | 2005-11-10 |
| CN100335808C (en) | 2007-09-05 |
| RU2005102818A (en) | 2005-08-10 |
| JP4628100B2 (en) | 2011-02-09 |
| KR20120099786A (en) | 2012-09-11 |
| JP2010270917A (en) | 2010-12-02 |
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